EP1619415A2 - Drehmomentwandler mit Überbrückungskupplung - Google Patents

Drehmomentwandler mit Überbrückungskupplung Download PDF

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Publication number
EP1619415A2
EP1619415A2 EP05254545A EP05254545A EP1619415A2 EP 1619415 A2 EP1619415 A2 EP 1619415A2 EP 05254545 A EP05254545 A EP 05254545A EP 05254545 A EP05254545 A EP 05254545A EP 1619415 A2 EP1619415 A2 EP 1619415A2
Authority
EP
European Patent Office
Prior art keywords
shell
clutch
power transmission
support portion
weld
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP05254545A
Other languages
English (en)
French (fr)
Other versions
EP1619415A3 (de
EP1619415B1 (de
Inventor
Naoto Sato
Toru Shimogaki
Tokuji Yoshimoto
Naomi Takagi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Yutaka Giken Co Ltd
Original Assignee
Yutaka Giken Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Yutaka Giken Co Ltd filed Critical Yutaka Giken Co Ltd
Publication of EP1619415A2 publication Critical patent/EP1619415A2/de
Publication of EP1619415A3 publication Critical patent/EP1619415A3/de
Application granted granted Critical
Publication of EP1619415B1 publication Critical patent/EP1619415B1/de
Ceased legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
    • F16H2045/0294—Single disk type lock-up clutch, i.e. using a single disc engaged between friction members

Definitions

  • the present invention relates to an improvement in a fluid transmitting device with a lock-up clutch, comprising: a turbine impeller having a shell; and a lock-up clutch including: a clutch piston; an annular spring accommodation groove formed in the clutch piston to accommodate a plurality of annularly-arranged damper springs; a plurality of first power transmission claws inserted between adjacent ones of the damper springs and secured to the clutch piston; a plurality of second power transmission claws inserted between adjacent ones of the damper springs so as to face the first power transmission claws, and having support portions which are connected to an outer peripheral surface of the shell of the turbine impeller via a weld formed by laser beams.
  • the present invention has been achieved in view of the above-mentioned circumstances and has an object to provide a fluid transmitting device with a lock-up clutch, wherein the support portions of the second power transmission claws and the shell of the turbine impeller can be easily welded together by laser beams, thereby easily performing a visual inspection as to whether the welding condition is good or not.
  • a fluid transmitting device with a lock-up clutch comprising: a turbine impeller having a shell; and a lock-up clutch including: a clutch piston; an annular spring accommodation groove formed in the clutch piston to accommodate a plurality of annularly-arranged damper springs; a plurality of first power transmission claws inserted between adjacent damper springs and secured to the clutch piston; a plurality of second power transmission claws inserted between adjacent damper springs so as to face the first power transmission claws, and having support portions which are connected to an outer peripheral surface of the shell of the turbine impeller via a weld formed by laser beams, wherein the weld is formed into a linear shape extending along a circumferential direction of the shell so that the weld is melted by the laser beams to extend from an outer surface of the support portion to an inner peripheral surface of the shell.
  • the laser welding machine and the shell are relatively rotated about an axis of the shell, thereby easily and reliably forming a linear weld of a desired length, and giving a desired bonding strength between the support portion and the shell.
  • the linear welds normally melt and reach an inner peripheral surface of the shell to form a linear discolored portion on the inner surface, it is possible to easily and reliably determine whether the condition of the weld is good or not only by a visual inspection as to presence or absence of the discolored portions, thereby contributing to an improvement in quality.
  • heat input to the welds formed by the laser beams is relatively small, it is possible to prevent any thermal distortion of the shell to provide a stable quality of the turbine impeller.
  • the linear weld is formed by a plurality of lines juxtaposed to each other with a space therebetween.
  • the linear weld extending in a circumferential direction of the shell are formed by the plurality of lines juxtaposed to each other with a space therebetween, thereby effectively increasing the bonding strength between the support portion and the shell, and improving the durability of the welds by dispersing stress over the welds during power transmission.
  • each of the second power transmission claws comprises a claw portion and a support portion integrally connected to the claw portion, a width of the support portion in a circumferential direction of the turbine impeller being larger that a width of the claw portion; and the support portion and the shell are connected together via the weld which has a length larger than the width of the claw portion.
  • the linear welds are formed longer than the width of the claw portion, thereby effectively increasing the bonding strength between the support portion and the shell.
  • the linear weld is formed so that opposite ends thereof do not reach edges of the support portion.
  • the opposite ends of the linear weld are terminated in front of the edges of the support portion, thereby preventing any chip-off by melting of the edges of the support portion by the laser beams, and preventing the strength from decreasing due to the chip-off by melting of the edges.
  • a gap surrounding the weld is provided between opposed faces of the support portion and the shell.
  • a gap surrounding the weld is provided between the opposed faces of the support portion and the shell, so that when the linear weld is formed by laser welding, gas generated from the molten weld can be rapidly discharged into the surrounding gap, thus preventing any blowholes from being generated by the gas to form a good-quality weld, which secures a desired and predetermined bonding strength between the support portion and the shell.
  • a radius of the opposed face of the support portion and a radius of the opposed face the shell differ from each other so that the support portion abuts on the outer peripheral surface of the shell at two points in opposite edges in radial directions of the shell, and the weld is formed in an intermediate portion between the two points.
  • a nitridation layer for securing abrasion resistance is formed on the second power transmission claws.
  • the nitridation layer is formed on the second power transmission claws to improve the abrasion resistance of the portions of the second power transmission claws which abut against the damper springs, and the nitrogen gas generated from the nitridation layer is smoothly discharged to the outside, thereby forming good welds.
  • a torque converter T as a fluid transmitting device includes a pump impeller 2, a turbine impeller 3 disposed to face the pump impeller 2, and a stator impeller 4 inserted between inner peripheral portions of the pump impeller 2 and the turbine impeller 3.
  • a circulation circuit 6 for transmitting a power by a working oil is defined between these three impellers 2, 3 and 4.
  • a power transmission cover 5 is integrally connected to an outer peripheral portion of the pump impeller 2 by welding to cover an outer side of the turbine impeller 3.
  • Starting ring gears 7 are welded to an outer peripheral surface of the power transmission cover 5.
  • a drive plate 8 coupled to a crankshaft 1 is secured to the ring gears 7 by bolts 9.
  • a thrust needle bearing 36 is interposed between a hub 3h of the turbine impeller 3 and the power transmission cover 5.
  • An output shaft 10 arranged coaxially with the crankshaft 1 is disposed at a central portion of the torque converter T.
  • the output shaft 10 is spline-fitted to the hub 3h of the turbine impeller 3, and rotatably supported on an inner peripheral surface of a hub 5h of the power transmission cover 5 with a bearing bush 18 interposed therebetween.
  • the output shaft 10 is a main shaft of a multi-stage transmission which is not shown.
  • a cylindrical stator shaft 12 is disposed around an outer periphery of the output shaft 10, and supports a hub 4h of the stator impeller 4 with a free wheel 11 interposed therebetween.
  • a bearing bush 13 is interposed between the output shaft 10 and the stator shaft 12, to permit the relative rotation of the shafts 10 and 12.
  • An outer end of the stator shaft 12 is non-rotatably supported at its outer end on a transmission case 14.
  • Thrust needle bearings 37 and 37' are interposed between the hub 4h of the stator impeller 4, and the hubs 2h and 3h of the pump impeller 2 and the turbine impeller 3.
  • An auxiliary-driving shaft 20 coupled to the hub 2h of the pump impeller 2 is relatively rotatably disposed around an outer periphery of the stator shaft 12, to drive an oil pump 21 for supplying the working oil to the torque converter T.
  • a clutch chamber 22 is defined between the turbine impeller 3 and the power transmission cover 5, to accommodate a lock-up clutch Lc capable of directly coupling the turbine impeller 3 and the power transmission cover 5 to each other.
  • a clutch piston 25 forming a main member of the lock-up clutch Lc is disposed in the clutch chamber 22, to divide the clutch chamber 22 into an inner chamber 22a on the turbine impeller 3 side and an outer chamber 22b on the transmission cover 5 side.
  • the clutch piston 25 has an annular web 25a bulging toward the power transmission cover 5 side and a rim 25b bending at an outer peripheral edge of the web 25a toward the turbine impeller 3 side.
  • the web 26 is provided with a friction lining 28 opposed to an inner surface of the power transmission cover 5.
  • the clutch piston 25 is slidably supported on an outer peripheral surface of the hub 3h of the turbine impeller 3 so as to axially move between a connected position where the friction lining 28 is pressed on an inner surface of the power transmission cover 5 and a disconnected position where the friction lining 28 is spaced apart from the inner wall.
  • a torque damper Dp is also disposed in the clutch chamber 22 to bufferingly connect together the clutch piston 25 and the turbine impeller 3.
  • the torque damper Dp comprises: an annular spring holding member 30 fixed to the clutch piston 25 by a rivet 35 to define an annular spring accommodation groove 31 in cooperation with the rim 25b of the clutch piston 25; a plurality (three in the illustrated example) of annularly-arranged coiled damper springs 32 accommodated in the spring accommodation groove 31; a plurality (the same number as the damper springs 32) of first power transmission claws 33 formed on the spring holding member 30 and inserted between the adjacent damper springs 32; and a plurality (the same number as the damper springs 32) of second power transmission claws 34 welded on an outer peripheral surface of a shell 3s of the turbine impeller 3, opposed to the first power transmission claws 33 and inserted between the adjacent damper springs 32.
  • the annular spring holding member 30 comprises a plurality of sector pieces 30a circumferentially divided at the central portions of the first power transmission claws 33.
  • a nitridation layer for securing abrasion resistance is formed beforehand on a surface of each of the second power transmission claws 34.
  • a first oil passage 40 is provided at the central portion of the output shaft 10 to communicate with the outer chamber 22b of the clutch chamber 22 via a side aperture 39 and the thrust needle bearing 36.
  • a second oil passage 41 is defined between the auxiliary machine driving shaft 20 and the stator shaft 12 to communicate with an inner peripheral portion of the circulating circuit 6 via the thrust needle bearings 37, 37' and the free wheel 11.
  • the first oil passage 40 and the second oil passage 41 are arranged to be alternately connected, through a lock-up control valve 42, to a discharge side of the oil pump 21 and an oil sump 43.
  • the lock-up control valve 42 is controlled by an electronic control unit (not shown) so as to connect the first oil passage 40 to the discharge port of the oil pump 21, and on the other hand, to connect the second oil passage 41 to the oil sump 43.
  • a torque output from the crankshaft 1 of the engine is transmitted through the drive plate 8 and the power transmission cover 5 to the pump impeller 2 to rotate the pump impeller 2, and when the oil pump 21 is also driven, a working oil discharged by the oil pump 21 flows from the lock-up control valve 42 sequentially via the first oil passage 40, the transverse bore 39, the thrust needle bearing 36 and the outer and inner chamber 22b and 22a of the clutch chamber 22 into the circulation circuit 6 to fill the circuit 6, and thereafter flows via the thrust needle bearings 37 and 37' into the second oil passage 41, and returns through the lock-up control valve 42 to the oil sump 43.
  • the pressure in the outer chamber 22b is higher than that in the inner chamber 22a in virtue of the flow of the working oil as described above, and the clutch piston 25 is retracted away from an inner wall of the power transmission cover 5 by a difference between the pressures in the outer and inner chamber 22b and 22a.
  • the lock-up clutch Lc is in a turned-off state, to permit the relative rotation of the pump impeller 2 and the turbine impeller 3. Therefore, when the pump impeller 2 is rotatingly driven from the crankshaft 1, the working oil filling the circulation circuit 6 is circulated in the circulation circuit 6 as shown by an arrow, whereby the rotational torque of the pump impeller 2 is transmitted to the turbine impeller 3 to drive the output shaft 10.
  • stator impeller 4 If amplification action of torque occurs between the pump impeller 2 and the turbine impeller 3 at this time, an accompanying reaction force is exerted on the stator impeller 4, so that the stator impeller 4 is fixed by a locking action of the free wheel 11.
  • stator impeller 4 rotates in the same direction together with the pump impeller 2 and the turbine impeller 3 due to reverse rotation of the torque which the stator impeller 4 receives, while idling the free wheel 11.
  • the operation of the lock-up control valve 42 is changed by the electronic control unit.
  • the working oil discharged from the oil pump 21 flows from the lock-up control valve 42 through the second oil passage 41 into the circulating circuit 6, fills the circuit 6, then flows to the inner chamber 22a of the clutch chamber 22, and also fills the inner chamber 22a.
  • the outer chamber 22b of the clutch chamber 22 is opened to the oil sump 43 via the first oil passage 40 and the lock-up control valve 42, the clutch chamber 22 has a pressure in the inner chamber 22a higher than that in the outer chamber 22b.
  • the plurality of second power transmission claws 34 arranged along a circumferential direction of the shell 3s are each separate and independent.
  • Each of the second power transmission claws 34 comprises: aclawportion34aopposed to the first power transmission claws 33 and inserted between the adjoining damper springs 32; and a rectangular support portion 34b integral with the base of the claw portion 34a.
  • Each of the second power transmission claws 34 is generally T-shaped and is made by punching a steel plate.
  • the width A of the support portion 34b along a circumferential direction D of the turbine impeller 3 is set larger than the width B of the claw portion 34a.
  • the support portion 34b is bonded to the outer peripheral surface of the shell 3s of the turbine impeller 3 via the welds 40 formed by laser beams L applied by a laser welding machine W.
  • the welds 40 are formed linearly along a circumferential direction of the shell 3s so that the welds 40 are melted by the laser beams L and extend from the outer surface of the support portion 34b to the inner peripheral surface of the shell 3s.
  • the laser welding machine W and the shell 3s are relatively rotated about an axis of the shell 3s, thereby easily and reliably forming linear welds 40 of a desired length, and giving a desired bonding strength between the support portion 34b and the shell 3s.
  • the linear welds 40 normally melt and reach the inner peripheral surface of the shell to form linear discolored portions on the inner surface, it is possible to easily and reliably determine whether the condition of the welds 40 is good or not only by a visual inspection as to the presence or absence of the discolored portions, thereby contributing to an improvement in quality.
  • heat input to the welds 40 formed by the laser beams L is relatively small, it is possible to prevent any thermal distortion of the shell 3s to provide a stable quality of the turbine impeller 3.
  • the linear weld 40 extending in a circumferential direction D of the shell 3s is formed into a plurality of parallel lines (two lines in the illustrated example) with a space therebetween, and the length C of the welds 40 is set longer than the width B of the claw portion 34a. Further, opposite ends of each weld 40 are terminated in front of edges of the support portion 34b.
  • the plural lines of linear welds 40 extending along the circumferential direction D of the shell 3s and longer than the width B of the claw portion 34a, can effectively increase the bonding strength between the support portion 34b and the shell 3s, and the durability of the welds 40 can be improved by dispersing stress over the welds 40 during power transmission.
  • opposite ends of the welds 40 are terminated in front of edges of the support portion 34b, thereby preventing chip-off by melting of the edges of the support portion 34b by the laser beams L to prevent the strength from decreasing due to the chip-off by melting of the edges, so that the welds 40 can bear a large torque transmission.
  • a gap g surrounding the welds 40 is provided between opposed faces of the support portion 34b and the shell 3s.
  • a radius of curvature r of a curved face of an inner peripheral surface of the support portion 34b opposed to the shell 3s along an arrangement direction of the plural lines of welds 40 is set smaller than a radius of curvature R of a corresponding outer peripheral surface of the shell 3s.
  • the support portion 34b when the support portion 34b is superposed on the outer peripheral surface of the shell 3s in laser welding, the support portion 34b abuts on the outer peripheral surface of the shell 3s at two points in opposite edges along the arrangement direction of the welds 40, to provide a gap g on the other portions between the support portion 34b and the outer peripheral surface of the shell 3s.
  • a nitridation layer for securing abrasion resistance is formed beforehand on the second power transmission claw 34, nitrogen gas generated from the nitridation layer can be smoothly discharged into the gap g around the welds 40, thus preventing any blowholes from being generated by the gas to form good-quality welds 40, thereby securing a desired and predetermined bonding strength between the support portion 34b and the shell 3s.
  • the plurality of second power transmission claws 34 are each separate and independent, a large number of second power transmission claws 34 can be punched out of a steel plate with good yield. Moreover, by freely setting the number and the fitting pitch of the second power transmission claws 34 to be used in correspondence to the specification of a torque converter T, they can be applied to various types of torque converters T, thus greatly reducing the manufacturing cost. Also, since the plurality of second power transmission claws 34 are dispersedly arranged on the outer peripheral surface of the turbine impeller 3, no obstruction to the flow of working fluid is present therebetween, thereby smoothening the flow of working fluid to the lock-up clutch Lc, to contribute to an increase in the responsibility.
  • FIG. 5 A second embodiment of the present invention as shown in FIG. 5 will now be described.
  • the arrangement of the second embodiment is same as that of the first embodiment, except that support portions 34b of a plurality of annually-arranged second power transmission claws 34 are integrally connected to each other via connecting band portions 41 having a width narrower than that of the support portions 34b. Therefore, the support portion 34b of each of the second power transmission claws 34 is bonded to an outer surface of a shell 3s of a turbine impeller 3 via plural lines of linear welds 40 formed by laser beams L, as in the first embodiment.
  • the parts in FIG. 4 corresponding to those of the first embodiment are denoted by the reference numerals same as those of the first embodiment, and the description thereof is omitted.
  • the support portions 34b of the plurality of second power transmission claws 34 are annually connected via the connecting band portions 41, there is no need to use a positioning fixture for mutually positioning the plurality of second power transmission claws 34 when the support portions 34b are laser welded to the shell 3s, thus improving the efficiency of welding operation.
  • the width of the connecting band portions 41 is narrower than that of the support portions 34b, thereby minimizing an increase in weight due to the connecting band portions 41.
  • the present invention is not limited to the above-mentioned embodiments, andvariousmodifications in design maybe made without departing from the subject matter of the invention.
  • the present invention is applicable to a fluid coupling without any stator impeller.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Laser Beam Processing (AREA)
  • Mechanical Operated Clutches (AREA)
EP05254545A 2004-07-21 2005-07-21 Drehmomentwandler mit Überbrückungskupplung Ceased EP1619415B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2004212488A JP4530750B2 (ja) 2004-07-21 2004-07-21 ロックアップクラッチ付き流体伝動装置

Publications (3)

Publication Number Publication Date
EP1619415A2 true EP1619415A2 (de) 2006-01-25
EP1619415A3 EP1619415A3 (de) 2009-07-29
EP1619415B1 EP1619415B1 (de) 2011-03-30

Family

ID=35058962

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05254545A Ceased EP1619415B1 (de) 2004-07-21 2005-07-21 Drehmomentwandler mit Überbrückungskupplung

Country Status (5)

Country Link
US (1) US7322454B2 (de)
EP (1) EP1619415B1 (de)
JP (1) JP4530750B2 (de)
CN (1) CN1724900B (de)
DE (1) DE602005027150D1 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007315496A (ja) * 2006-05-25 2007-12-06 Yutaka Giken Co Ltd 船外機
EP1947369A1 (de) * 2007-01-22 2008-07-23 Honda Motor Co., Ltd Flüssigkeitsübertragungsvorrichtung
EP1860347A3 (de) * 2006-05-25 2008-08-27 Yutaka Giken Co., Ltd. Aussenbordmotor

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BRPI0708543A2 (pt) * 2006-03-07 2011-05-31 Daikin Ind Ltd método de produzir compressor, e compressor
DE102007017430B4 (de) * 2006-05-01 2017-06-08 Schaeffler Technologies AG & Co. KG Außenplatte mit Antriebszunge für Bogenfedern für einen Dämpfer eines Drehmomentwandlers
JP5078535B2 (ja) * 2007-10-10 2012-11-21 株式会社エクセディ ロックアップ装置およびそれを備えた流体式トルク伝達装置
WO2010041137A1 (en) * 2008-10-10 2010-04-15 Toyota Jidosha Kabushiki Kaisha Fluid transmission device
JP5728186B2 (ja) * 2010-09-13 2015-06-03 アイシン機工株式会社 ドライブプレートおよびドライブプレートのリングギヤ部材
JP5556551B2 (ja) * 2010-09-30 2014-07-23 アイシン・エィ・ダブリュ株式会社 流体伝動装置
EP2700847B1 (de) * 2011-04-18 2017-10-11 Toyota Jidosha Kabushiki Kaisha Verfahren und Vorrichtung zur Herstellung einer Fahrzeugkraftübertragungsvorrichtung
JP2012237418A (ja) * 2011-05-13 2012-12-06 Yutaka Giken Co Ltd ロックアップクラッチ付き流体伝動装置
JP5584249B2 (ja) * 2012-04-10 2014-09-03 株式会社エクセディ トルクコンバータのロックアップ装置
DE102017124961B3 (de) * 2017-10-25 2018-09-13 Kleemann Gmbh Antriebssystem zum Antrieb eines Brechers und Verfahren zum Betrieb eines Brechers

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JP3001853B2 (ja) 1997-05-23 2000-01-24 マンネスマン ザックス アクチエンゲゼルシャフト ねじり振動ダンパを有するロックアップクラッチ
US20030106756A1 (en) 2001-11-12 2003-06-12 Naoto Sato Fluid transmission system with lock-up clutch

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JPH0744384Y2 (ja) * 1989-02-20 1995-10-11 日産自動車株式会社 ディスクロードホイール
JPH0741586Y2 (ja) * 1991-11-18 1995-09-27 日本軽金属株式会社 表面処理材連結用レーザ溶接装置
JPH0947887A (ja) * 1995-08-04 1997-02-18 Tokai Rubber Ind Ltd 筒形巻き金具の製造方法
DE10050729A1 (de) * 2000-10-13 2002-04-25 Zf Sachs Ag Hydrodynamische Kopplungseinrichtung
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JP3001853B2 (ja) 1997-05-23 2000-01-24 マンネスマン ザックス アクチエンゲゼルシャフト ねじり振動ダンパを有するロックアップクラッチ
US20030106756A1 (en) 2001-11-12 2003-06-12 Naoto Sato Fluid transmission system with lock-up clutch

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007315496A (ja) * 2006-05-25 2007-12-06 Yutaka Giken Co Ltd 船外機
EP1860347A3 (de) * 2006-05-25 2008-08-27 Yutaka Giken Co., Ltd. Aussenbordmotor
US7578713B2 (en) 2006-05-25 2009-08-25 Yutaka Giken Co., Ltd. Outboard engine system
EP1947369A1 (de) * 2007-01-22 2008-07-23 Honda Motor Co., Ltd Flüssigkeitsübertragungsvorrichtung
US8863923B2 (en) 2007-01-22 2014-10-21 Honda Motor Co., Ltd Fluid transmission device

Also Published As

Publication number Publication date
JP4530750B2 (ja) 2010-08-25
DE602005027150D1 (de) 2011-05-12
CN1724900A (zh) 2006-01-25
US7322454B2 (en) 2008-01-29
EP1619415A3 (de) 2009-07-29
JP2006029531A (ja) 2006-02-02
US20060016654A1 (en) 2006-01-26
EP1619415B1 (de) 2011-03-30
CN1724900B (zh) 2010-10-13

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